Machine tool transmission



Oct. 25, 1949. E- J- KE NEY L 2,486,294

- MACHINE TOOL TRANSMISSION Original Filed June 9, 1938 1O Sheets-Sheet 1 INVENTORS E. J. KEARNEY, fiezeaxa/ Q W. CARPENTER JR, 4%;

JBARMITAGE 8. WM. POHL ATTORNEY 1949' E. J. KEARNEY ETAL MACHINE TOOL TRANSMISSION 1O Sheets-Sheet 2 Original Filed June 9, 1938 INVENTORS EVJ KEARNEY fleceose/ 0. CARPENT'ER JRMMI; .J.B.AR| E WMPOHL ATTORNEY Oct. 25, 1949. KEARNEY ETAL 2,486,294 V MAGHINE TOOL TRANSMISSION 1O Sheets-Sheet 3 INVENTORS E.J.KEARNE CAR ,M; MTAGE & W.M.POHL

Original Filed June 1938 ATTORNEY 10 Sheets-Sheet 4 xll 1949' E. J. KEARNEY ETAL MACHINE TOOL TRANSMISSION Original Filed June 9, 1938 Oct. 25, 1949. E. J. KEARNEY ETAL.

MACHINE TOOL TRANSMISSION Original Filed June 9; 1938 10 Sheets-Sheet 5 RS Yflezeaed OWCARPENTEFi Uni/0; .ARIWAIZE Z w OHL ATTORNEY I NVE NTO E: J. KEARNE' Oct. 25, 1949. E- J- KEARNEY ETAL MACHINE TOOL TRANSMISSION l0 Sheets-Sheet 7 Original Filed June 9 1938 FIG. l3

FIG. l4

OINVENT 7 E. o.w NTER JR, 404

J.B.ARMITAGE & BY W ATTORNEY Oct. 25, 1949. E. J. KEARNEY ET AL MACHINE TOOL TRANSMISS IQN 10 Sheets-Sheet 8 Original Filed June 9, 1938 FIG I6 INV KEAREIZIIEI CARPENTER Ed. 7 O.W. J. B. ARM ITAGE BY ATTORNEY Oct. 25, 1949. E. J. KEARNEY ETAL MACHINE TOOL TRANSMISSION l0 Sheets-Sheet 9 Original Filed June 9, 1938 2% v N Mm E m N RKRM R m fl T. NWT m ERNE, A vmnsfl mW am 5 @JW 'I-/ 7 1 H- N I u-nn I v ,7,

Oct. 25, 1949.

E. J. KEARNEY ET AL 2,436,294

MACHINE TOOL TRANSMISSION Original Filed June 9, 1938 I 10 Sheets-Sheet 1O ATTORNEY Patented Oct. 25, 1949 UNITED STATES PATENT OFFICE MACHINE TOOL TRANSMISSION consin Original application June 9, 1938, Serial 'No. 212,704, now Patent No. 2,355,082, dated August 8, 1944. Divided and this application July 6, 1944, Serial No. 543,682

13 Claims.

This invention relates generally to machine tools, and more particularly to transmission and control apparatus for an automatically operating milling machine.

The present specification constitutes a division of application Serial No. 212,704, filed June 9, 1938, now Patent No. 2,355,082, dated August 8, 1944.

In order to operate a milling machine at maximum production efiiciency, successive workpieces must be fed to the milling cutter in such a manner that the delay occurring between the completion of one workpiece and the beginning of the cutting operation on the next workpiece is reduced to the minimum. According to a generally practiced method of operating a standard milling machine, a workpiece is moved at rapid traverse rate from a loading position in direction to approach the cutting zone; then it is fed past the milling cutter in the cutting stroke; then it is withdrawn by moving it past the cutter a second time in the opposite direction at rapid traverse rate to return it to the loading position. To avoid having the finished workpiece gouged by the cutter in returning past it to the loading position, it is the usual practice to stop the cutter spindle at the end of the feed stroke, the cutter remaining stationary until the beginning of the succeeding feed stroke. This method of operation is time-consuming and is otherwise unsatisfactory, the work being scratched by the cutter, in some instances, in moving past it on the return stroke. Because of these shortcomings, it has been generally recognized that milling machines should be so constructed as to provide for leading the finished workpiece away from the cutting zone, without withdrawing it past the cutter.

It is, therefore, a general purpose of the present invention to provide an improved automatically operating milling machine capable of maximum production in machining workpieces.

Another purpose of the invention is to provide .a milling machine capable of effecting an automatic cycle of operations so correlated that the cutting action upon successive workpieces is performed in a substantially continuous manner.

Another object is to provide an improved milling machine adapted to move successive workpieces past a rotating milling cutter continuously Another object is to provide an improved hy draulic control system for a machine tool.

Another object is to provide improved automatic clamping mechanism for holding workpieces on a machine tool.

Another object is to provide means for automatically clamping workpieces prior to feeding them toward a milling cutter and automatically unclamping the finished workpieces after the cutting operation.

Another object is to provide fluid operated work clamping apparatus having means for adjusting the clamping pressure.

Another object is to provide a machine tool having hydraulically actuated mechanism carried by a movable member and controlled in response to the position of the movable member.

Another object is to provide a machine tool of the rotary table type having valve means associated with the pivotal support for the table and functioning in response to rotation of the table to control fluid ope-rated mechanism carried by the table. 7

Another object is to provide hydraulic control mechanism for apparatus carried by a rotating member of a machine tool, including a pump arranged for bodily movement with said rotating member.

According to this invention, an automatic milling machine is arranged to receive workpieces at a loading station some distance from the milling cutter and to advance-the workpieces into engagement with the cutter successively in manner to effect a substantially continuous machining operation, the finished workpieces being led away from the cutting zone back to the loading position, without moving across the cutter a second time. For supporting and moving the workpieces, there is provided a continuously rotating table carrying a plurality of movably mounted work holders which cooperate with a cam track in manner to move successive workpieces through the cutting zone along a straight line path. The work holders include clamping means actuated by fluid pressure and controlled in accordance with the angular position of the table. The continuously rotating table is actuated alternately at rapid traverse rate and at feed rate, the rapid traverse movement functioning to quickly advance a workpiece to the cutting zone and to rapidly lead a finished workpiece away from the cutting zone.

The foregoing and other objects of this invention, which will become more fully apparent from the following detailed specification, may be chine shown in Figure 1, with parts broken away to show the internal mechanism;

Figure 3 is a view in vertical longitudinal :section through the machine, taken approximately along the plane represented by the line 3-3 in Figure 2 and showing the driving mechanism;

Figure 4 is a view in horizontal section of part of the driving mechanism, taken generally along the planes represented by the line 44 in Figures 3 and 6;

Figure 5 is a detailed view, partly in section, of an element of the driving mechanism taken along the plane :representedby theline 5-5 in Figure 4;

Figure 6 :is .a view largely in vertical section,

of part of the driving mechanism taken approximately along the plane represented by the line it- 6 in Figure 4 :and showing the table controlling clutches;

Figure? is a detailed view in horizontal crossseotion of the clutch mechanism, taken along the line 'l'! in Figure 6;

Figures :8, 9 and are fragmentary detailed 'yiews cross-section, taken along the lines 8-8,

99, and Ill-l0, respectively, in Figure 6 and showing elements of the various control clutches;

Figures 8A, 9A and 10A are views similar to Figures 8, 9 and 10, respectively, but showing the clutches shifted .to another position;

Figure ll is a view largely in vertical transverse section through the machine, taken generally along the plane represented by the line I I-H in Figure .31;

Figure 12 is a detailed fragmentary View in vertical section of selective mechanical control mechanism, taken approximately along the plane represented by the line I 2- l2 in Figure 4;

.Figure 13 is a fragmentary view of the rotary table mechanism taken in horizontal cross-section along the line l3l3 in Figure .11;

Figure 1.4:is another view in horizontal crosssection of the table mechanism, taken approximately along the plane represented by the line ill-l4 Figure 1.1 and showing the work guiding cams;

Figure .15 is a view in vertical section through one of the work holding yises, taken along the plane represented by the lines l5--'|5 in Figures .2, .3 and 13;

Figure 16 is a plan view of a-work holding vise constituting a modification .of the vise shown mounted on the machine table;

Figure 17 is 'a view of the modified vise taken vertical section along the plane represented by-the line IFL-H in Figure 16;

Figures l8, 19, .20, 21 and 22 are views in horizontal section through the hydraulic pumps and control valve in the table .gudgeon, taken respectively along the correspondingly numbered lines in Figure 11 Figure 23 is a partly diagrammatic illustration of selective hydraulic clutch controlling mechanism constituting a modification of the mechanical clutch controlling mechanism illustrated in Figure 12,;

Figure 24 is a view of the modified clutch control-ling mechanism horizontal section.

adjustably mounted tool spindle 32.

taken along the plane represented by the line 24-24 in Figure 23;

Figure 25 is a schematic diagram of the automatic hydraulic control circuit for the milling machine; and

Figure 26 an enlarged view of the stabilizing cylinder and piston mechanism shown at the top in Figure 25, the piston having been moved to its central position.

Referring more specifically to the drawings, Figures 1 and 2 thereof in particular show the general structure of the continuously operating automatic milling machine constructed in accordance with the principles of this invention that is particularly referred to herein by way of example. As there shown, the machine includes a frame that comprises essentially a bed or base 39 having secured at its back an upstanding spindle supporting column 3|, which carries an Rotatably mounted on the top of the bed 30 in front of the column BI is a horizontally disposed circular work supporting table 33 carrying a pair of work holding fixtures 34 and 35 disposed thereon in diametrically opposed relationship. As shown in Figures 3 and 11, the rotatable table 33 is provided with "a depending central gudgeon 36 that is journalled in the top of the bed 30 in manner to constitute a pivotal mounting for the table.

The two work holding fixtures 34 and 35 are supported on the table 33 in manner to be movable radially thereof, by means of a reciprocating cross slide 3"! that is slidably mounted diametrically of the table 33, as shown in Figure 2, the fixture being rotatably mounted near the respective ends of the slide. By this arrangement, the Work holding fixtures are movably mounted on the table 33 in such manner that when the table is rotated, the fixtures in turning with it maybe guided successively through the cutting zone along a predetermined path. For effecting this guiding action, each fixture is provided with two depending studs or arms 38 and 39, which carry rollers at their lower ends disposed to engage with and roll upon the straight surface of a the table is rotated, the fixtures each having a compound motion, by reason of the sliding and turning movements provided by its rotatable mounting on the reciprocating cross slide 31. 'lhis provides for feeding workpieces successively in the same direction 'along the straight line path through the cutting zone and then leading them away without the necessity of withdrawing them past the cutter, each workpiece following the closed path indicated by the dot-dash line 41 in Figure 2.

The cutter supporting spindle 32 is arranged to be adjusted relative to the work table 33, :both in Vertical direction and transversely of the path of movementof the work holding fixtures through the cutting zone. To provide for the vertical adjustment, the supporting spindle is carried by a spindle head 42., which is slidably mounted on the column 3|. The usual overarms 54 are slidably mounted in the upper part of the spindle head 42 in position to carry 'a depending arbor support 55, in which the endof an arbor 56 carrying .a cutter 57 is rotatably supported. Clamping bolts 58 are provided fo :clamping the overarms 54 in adjusted position in the spindle head.

In operating the machine'the work holding fixture, which happens to be in the forward position or loading station, may be loaded with a workpiece while the table is turning slowly at feed rate. At the end of the feeding stroke, the table is automatically turned at rapid traverse rate to cause the workpiece to approach quickly to a position closely adjacent to the rotating cutter 'B'I, the workpiece being clamped automatically, as the table is turned. The rate of table movement is then automatically changed back to feed rate, in order to feed the workpiece along the straight line path through the cutting zone in operative engagement with the cutter 51.

After the workpiece has passed across the cutter, the table is again automatically moved at rapid traverse rate in the same direction to quickly lead away the finished workpiece and bring it around to the forward position for unloading, a new workpiece in the other fixture meanwhile being moved simultaneously into position for feeding to the cutter. By this arrangement-the work table may be turned continuously in the same direction alternately at rapid traverse rate and at feed rate with the cutter rotating continuously at a predetermined speed to effect substantially continuous milling of successive workpieces.

Power for turning the work table 33 and for rotating the cutter spindle 32 is derived from an electric motor 6I, which is mounted in the lower part of the column 3|, as best shown in Figurel. Referring particularly to Figures 3 and 4, the shaft of the motor BI is operatively connected to a worm 62, which meshes with a horizontally disposed worm wheel 63 that is rotatably mounted in the column M. The Worm wheel 63 is internally splined and slidably engages a splined shaft 64, extending verticallyto and journalled in the spindle head 42 in manner to be movable vertically therewith, and constituting part of the transmission train for driving the tool spindle 32, as fully described in the previously mentioned Patent No. 2,355,082.

The transmission train for transmitting power from the motor for turning the work supporting table at a selected feed rate includes a spur gear 82 formed on the hub of the worm wheel 63, which rotates continuously whenever the motor is operating. As shown in Figure 4, the spur gear 82 meshes with a mating gear 83 on a vertical shaft 84 that is provided at its upper end with a removable gear 85 constituting part of a feed rate changing mechanism 86. The removable gear 85 meshes with a complementary removable gear 81 on a parallelly disposed vertical shaft 08, which also carries another removable gear 89 meshing in turn with a removable gear 99 on the upper end of a vertically disposed shaft 9|. The removable gears 85, 81, 89, and 90 of the rate changer 86 constitute a pick-off rate changing mechanism generally similar to the speed changer I2 and which may be adjusted by interchanging the gears or substituting other appropriate complementary pairs thereof to provide for turning the table 33 at the required feed rate, a cover plate or door being provided for affording convenient access to the removable gears for changing them.

The vertical shaft 9| of the rate changer is provided with a bevel gear 92, which meshes with a complementary bevel gear 93 on the outer end of a feed drive shaft 94, which is journalled in the bed 30 of the machine and carries at its inner end a feed worm 95. The feed worm 95 meshes irreversibly with a horizontally disposed worm wheel as that is rotatably mounted by means of anti-friction bearings in the bed 30 and is provided with an internal cylindrical clutching surface 91.

Disposed concentrically with the worm wheel 96 and journalled in the bed separately therefrom is a vertically disposed table driving shaft 98, which is provided at its upper end with a spur pinion 99 meshin with an internal or ring gear I09 secured beneath the lower outer edge of the table 33 and disposed concentrically with the central gudgeon 36. The table drivingshaft 98 has fixed on its lower end a driving collar or bushing 102 that is provided around its top edge with a plurality of sloping radially acting cam surfaces I03 constituting the internal member of an overrunning clutch I04. As best shown in Figures 4 and 6, a plurality of spring-pressed rollers I 05 are disposed between the cam surfaces E03 and the internal clutching surface 91 of the worm wheel 99, in such manner that the wheel is adapted to drive the shaft 93, when rotated in one direction, in a well known manner, the clutch 505i functioning to permit the shaft 98 to turn faster than the feed worm wheel 99, when the table is being driven at rapid traverse rate.

For turning the table at rapid traverse rate, there is provided a rapid traverse worm I0! disposed in alignment with the shaft of the motor I5! and operatively connected to the end of the worm 62 by means of an axially movable splined connection or joint I08, as shown in Figure 4. The rapid traverse Worm I01 meshes with a cooperating worm wheel I09, which is rotatably mounted by means of anti-friction bearings in the bed 30 below :and concentrically with the feed worm wheel 96. The rapid traverse worm wheel I09 is likewise provided with an internal cylindrical clutching surface I I0 for engagement'by rollers III, which cooperate with cam surfaces IIZ disposed around the lower edge of the driving collar I02, constituting a clutch or ratchet mechanism II 3 generally similar to the overrunning feed clutch I04, but arranged for positive selective engagement to drive the table in the same direction at rapid traverse rate with the clutch I04 overrunning. To effect selective operation of the clutch II3, the rollers I II are engaged by depending fingers of bars constituting a spacing cage I I4 formed on the lower end of a clutch shifting sleeve II5 that is disposed concentric with and encircles the driving collar I02. This arrangement permits positive selective disengagement of the clutch I I3 or positive engagement thereoffor operating the table at rapid I traverse pate.

Inasmuch as the table 33 and the work holding fixtures carried thereby constitute a rotating element having considerable inertia, it is desirable to provide means for absorbing the shock incurred when the rapid traverse clutch H3 is engaged suddenly. To this end, the rapid traversing worm I01 is mounted in manner to be free to slide endwise by reason of the splined connection I08, a spring I I8 being provided for normally retaining the worm in central position, relative to the ,worm wheel I09. To prevent the spring II8 from returning the worm I01 beyond its normal position or at excessive speed after the table has been accelerated, a dashpot H9 is provided at the other end of the worm, as shown in Figures 3 and 4. The dashpot functions to trap lubricating oil supplied from a reservoir I20 and to expel it through restricted openings in such 7 manner as to cushion the return movement of the worm.

In order to conserve time during the cutting cycle, it is desirable to have the workpiece approach as close as possible to the cutter at rapid traverse nate and ithen automatically change the rate of table movement to feed rate for feeding the work into engagement with the cutter'without delay. The promptness with which the workpiece may be fed into engagement with the roing the rate of movement from rapid traverse to L feed rate, the driving mechanism is equipped with a. synchronizing or decelerating positive roller clutch or ratchet mechanism I24 cooperating with the feed Worm wheel 96 and generally similar in structure to the rapid traverse clutch H3,

but disposed to operate in the opposite direction. The synchronizing or decelerating clutch I24 includes rollers I25 disposed to cooperate with cam surfaces I26, formed on an intermediate part of the driving collar I02, in manner to be forced thereby into engagement with an internal cylindrical clutching surface I2I in the lower part of the :feed rate worm wheel 96. For engaging or disengaging the synchronizing clutch I24, a

spacing cage I28 similar to the cage H4 is provided on the upper end of the clutch actuating sleeve I I5, the arrangement being such that when the sleeve H5 is turned to disengage the rapid traverse clutch II3, it is moved in the direction to engage the synchronizing clutch I24, and since the clutches act oppositely, they may thus be engaged alternatively.

When the synchronizing clutch I24 is engaged, it positively prevents rotation of the table driving shaft '98 at a rate faster than the rate that is established by the feed worm wheel 96. Since the worm wheel 96 and its cooperating feed worm 95 constitute an irreversible drive mechanism, the; inertial forces of the rotating table 33 are exerted through the synchronizing clutch I24 upon the .feed worm wheel 35 and against the worm 95 in a manner to quickly and positively check the rotative velocity of the table :33 and reduce it to the rate of movement corresponding to the feed rate at which the feed worm wheel 96 is turning, as determined by the feed rate changer 86. As the table driving torque is then exerted through the feed rate over-running clutch I04, the two roller clutches acting in opposite-directions tend to lock the feed worm wheel 96 to the shaft 98 with a positive grip.

The .fact that the feed rate driving worm and Worm wheel mechanism is irreversible and that it is positively coupled to the table :by the overrunning clutch and the synchronizing clutch, makes it possible to operate the machine in a manner to effect climb cutting of workpieces without danger of the table being-pulled ahead by the rotating cutter at a rate faster than the predetermined feed rate.

Circumferential shifting movement of the clutch Shifting sleeve H5 relative to the driving collar 12 is eiiected by means of an axially movable shifting collar I3SI, which encircles the clutch sleeve, .as shown in Figures 3, 6, and 7,

and is provided with diametrically opposed inlwardly projecting pins I32. As shown in Figure '7, the pins I32 extend through slots I33 in the clutch sleeve H5 into axially disposed slots I34 in the driving collar I02, the arrangement being such that the shifting collar I3I is caused to rotate with the driving collar I62 and the. shaft '98, but is free to be moved axially relative thereto along the slots I34. As shown in Figure 6, the slots I33 in the clutch sleeve H5 are angularly disposed or pitched in such manner that when the shifting collar I3I moves the pins I32 along the axially disposed slots I34 in the driving collar I02 from end to end thereof, the clutch sleeve I13 is caused to turn relative to the driving collar through a sufiicient angle to disengage one of the roller clutches and to engage the other clutch, thereby providing a convenient and effective control mechanism for the roller clutches.

When: the shifting collar I3I is moved to its upper position, as shown in Figure 6, the clutch shifting sleeve H5 is turned in manner to disengage the rapid traverse driving clutch H3, the spacing cage I I4 on the lower end thereof moving the clutch rollers III into the deep portion of the cam grooves H2, as shown in Figure 10.

With the rapid traverse driving clutch disengaged, the table is driven at feed rate, by means of the over-running feed rate clutch I04, a spring I36 acting upon a spacing cage I31 to force the clutch rollers I05 into wedging engagement between the cam surfaces I93 on the driving collar and the cylindrical clutching surface 91 Within the feed Worm 06 to effect a driving connection in the manner indicated in Figure 8.

If it is desired to operate the table at rapid traverse rate, the shifting collar I3I is moved downward, thereby causing the clutch sleeve II5 to turn counter-clockwise, relative to the driving collar I52, by reason of the action of the pins I32 in the angular slots I33 and the vertical slots I34. This results in moving the rollers III of the rapid traverse clutch into wedging engagement between the cam faces H2 and the clutch su-rilace I I0, as shown in Figure 10A. The rollers III then effect a connection between the rapid traverse worm wheel I09 and the table driving shaft 98, causing the shaft to rotate faster than the feed Worm wheel 96, with the result that the overrunning clutch I64 becomes disconnected or overruns with its rollers disengaged, as indicated in Figure 8A.

In effecting a sudden change in the rate of movement of the table from rapid traverse to feed rate at an accurately predetermined position, the clutch sleeve I I5 is caused to turn clockwise by moving the shifting collar I3I upward to the position shown in Figures 3 and 6, thereby disengaging the rapid traverse clutch H3, as shown in Figure 10 and immediately efiecting engagement of the synchronizing clutch I24, as shown in Figure 9. As previously explained, this quickly reduces the rate of movement of the table tothe speed at which the overrunning feed clutch I04 engages, whereupon the movement of the table is continued at the predetermined feed rate.

In order that the changes in the rate of movement of the table may be caused to occur automatically at accurately predetermined positions, automatic trip mechanism arranged to be actuated by trip dogs carried by the rotary table is provided. As may be seen in Figures 2, 3 and 11, the ring gear I00 secured beneath the table is provided on its periphery with a circumfenentially disposed T-slot I4I, adapted to receive trip dogs. As shown in Figure 2, a trip dog I42 in the T-slot MI is adapted to engage a trip arm I43 mounted on the upper end of a trip shaft I44 that is vertically disposed at its lower end. with an arm I45, which carries a shoe I46 engaging a notch in a horizontally disposed push rod I41 slidably mounted in the machine bed 30, as shown in Figure 4. The push rod I41 is provided at its other end with a notch. I48, which engages the upper end of an arm I49 on a shaft I50, as shown in Figure 5. The shaft I50 is rotatably mounted in the machine bed 30 as shown in Figures 3 and 4, and is provided at its inner end with a shifting fork II carrying shoes I52, which engage a groove I53 in the periphery of the clutch shifting collar I3I, as shown in Figures 6 and '1. The shoes I52 engage the groove I53 in manner to permit the collar to rotate with the clutch mechanism by the shaft 98, and upon turning movement of the shaft I50, they operate to move the shifting collar vertically.

The arrangement of the automatic trip mechanism is such that when the dog I42 engages the arm I43 and forces it outward, the shaft I44 is turned in manner to effect movement of the shifting collar I3I to its upper position, th ereby disengaging the rapid traverse driving clutch H3 and engaging the synchronizing clutch I24 in manner to cause the rate of movement of the table to be reduced to feed rate substantially instaneously. For automatically effecting en gagement of the rapid traverse drive, another dog I55, provided in the T-slot MI, is operative to engage a trip lever I56 mounted on the upper end of a vertical shaft I51, shown in Figure 4, and provided with a pinion I58 meshing with a gear segment I59 fixed on the shaft I44, the arrangement being such that the trip arm I56, when. engaged and moved outward by the dog I55, turns the shaft I44 in direction opposite to that in which it is turned by outward movement of the arm I43, thereby causing the shifting coll-ar I3I to be moved downward to disengage the synchronizing clutch I24 and to engage the rapid traverse rate driving clutch H3. As shown in Figure 4, the arm I45 is provided at its outer end with angularly disposed cam faces I60 constituting a detent point I6I that is engaged by a roller I62 on the end of a pivoted arm I63. The arm I 63 is urged by a spring I64 in direction causing the roller I62 to act on one or the other of the cam faces I60, in manner to force the detent arm I45 in one or the other direction to positively engage a selected one of the roller clutches. By this arrangement, any wear which occurs in the clutches is automatically taken up by the spring I64. Further, the spring I64 effects engagement of one or the other clutch as soon as the arm I45 has been moved by the trip arm I43 or the trip arm I55 a sumcient distance to move the centrally disposed detent point I6I at the junction of the cam faces I60, beneath the roller I62, the roller I62 then being forced against the other cam face by the spring I64, causing the arm I45 to quickly complete its movement.

Because of the action of the synchronizing clutch I24 in quickly reducing the'rate of movement of the table, the feed dog I 42 may be set at such position that a workpiece held in the work holder 35, for instance, may be caused to approach at rapid traverse rate to a position quite close to the cutter before the rate of move- 10 ment is changed to feed rate. By this arrangement, loss of time in moving the table at feed rate for a considerable distance, before the work engages the cutter, is avoided. Since the two work holders 34 and 35 are disposed at opposite ends of the cross slide, the table is provided with two sets of trip dogs I42 and I55, disposed at diametrically opposed positions thereon, as shown in Figure 2. The accurate action of the trip mechanism in cooperation with the positively actuated roller clutches constitutes, in effect, an indexing operation definitely positioning each successive workpiece relative to the cutter.

The angular distances through which the table is turned at feed rate and at rapid traverse rate, respectively, with the trip dogs in the position shown, are set off by the dot-dash lines I65 and I66 in Figure 2. As there indicated, the table is turned through the angle A at feed rate in moving the forward work holder through the loading position, and is then turned at rapid traverse rate through the angle B in moving the loaded work holder up to the feeding position adjacent to the cutter. In feeding the workpiece across the cutter, the table turns through the angle C at feed rate and, after the cutting operation is completed, the table is moved at rapid traverse rate through the angle D to lead the finished workpiece away from the cutting zone and bring it around to the forward station for unloading.

Since the operations of unloading the finished workpiece and replacing it with a fresh workpiece are performed by the machine attendant during the time that another workpiece is being fed through the cutting zone, it sometimes happens that the time taken by the table in moving through the cutting stroke is not sufficient for completion of the loading operation. In this event, the machine attendant may prolong the feeding movement and prevent or delay shifting to the rapid traverse rate of movement, as long as may be necessary to complete the loading operation by merely depressing a pedal I1I, pivotally mounted on the front of the machine, as shown in Figures 1 and 11.

The pedal IN is connected by a link I12 to an arm I13 mounted on a shaft I14, which extends horizontally into the machine bed 30, as shown in Figure 4. The shaft I14 carries a depending arm I15, the lower end of which engages a notch I16 in a plunger I11 that is slidably mounted in the bed 34, as shown in Figures 4, 11, and 12. When the pedal I1I is depressed, the shaft I14 is turned clockwise, as seen in Figure 11, and the plunger I11 is moved to the left beneath the shifting collar I3I, in manner to prevent it from being shifted downward from the feed rate position to the rapid traverse rate position, thereby restraining the mechanism from operating at rapid traverse rate. Since the final movement of the shifting collar I3I is effected by the spring I64 acting on the detent point IBI of the arm I45, interference with the movement of the shifting collar by the plunger I1'I does not obstruct the action of the trip dogs I42 and I55. To this end, the trip mechanism may be so adjusted that the shifting collar I3I is not moved a sufficient distance to shift the clutches until after the detent point I6I passes the spring urged roller I62. For this purpose, the arm I49 which is engaged by the push rod I41, as shown in Figure 5, is rotatably mounted on'the shaft I50 and arranged to be engaged by set screws I8I and I82 carried in a bifurcated bracket I83 keyed on the shaftv I50, the arrangement being such that the angu- 11 lar relationship of the arm I49 and the shaft I59 may be adjusted to effect precisely the desired action of the trip mechanism.

The inner or forward end of the plunger I'l'l is provided with a spring urged rotatable bolt or roller 184 that enters beneath the shifting collar I3! as shown in Figure 12, when the pedal is depressed. In the event that the collar I3I is being shifted toward, or has already been shifted into rapid traverse position before the pedal is depressed, the roller I84 may not pass beneath the collar, but may first be forced against it yieldingly, by means of a spring I85, the end of the roller engaging the periphery of the collar. As the collar I3! turns with the table driving. shaft, the roller will then be forced by the spring into one or another of a plurality of cam notches I86 in the lower edge of the collar, each of whichpresents an inclined face I87 adapted to engage the roller I99 and coact with it in manner to lift the collar, thereby shifting the clutches from rapid traverse position to feed position. The end of the roller I89 then passes farther beneath the collar I31 into rolling engagement with a horizontal circular face I89 thereof, as shown in Figure 12, thereby retaining the collar in its upper or feed position. After the loading operation has been completed, the attendant releases the pedal Ill, and a spring I99 on the end of the plunger .lTl opposite from the clutch mechanism withdraws the roller from beneath the collar I3I, thereby permitting the detent spring I99 to complete the clutch shifting operation previously initiated to engage the rap-id traverse drive, a collar I99 being provided on the plunger I'll to limit its outward movement, as shown in Figure 4.v

Referring particularly to Figures 3 and 11, the

work carrying table 33 is rigidly supported for r tation in a, horizontal plane by means of bearing surfaces l94 disposed on the top of the bed 39 in position to support the outer edges of the table closely adjacent to the driving ring gear I99. The central gudgeon 39, which pivotally supports the table is downwardly tapered in shape and is rotatably journalled in a complementary tapered pivot bearing or sleeve I99, adjustably mounted in the bed 39 of the machine. To insure accurate and rigid support of the table in its pivot bearing, the lower end of the tapered gudgeon 39 is provided with a retaining nut I91, which may be turned to hold the gudgeon in snug engagement with the tapered bearing sleeve I 99, the sleeve being adjustably positioned in the bed 39 by means of shims I 99 for establishing the proper fit with the gudgeon and held in adjusted position by bolts I99.

As may best be seen in Figures 11 and 15, the work holder carrying slide 3'! is mounted for movement diametrically of the table 33, by means of ways 299 on the top of the table, which are engaged by gibs 29! on the slide to constitute a sliding bearing or connection of well known type. Asbest shown in Figure 3, each of the work holding fixtures 34 and 35 is rotatably mounted near one end of the slide 31, by means of vertically spaced anti-friction bearings 293 and 294 in such manner that it is rigidly supported on the slide and yet isfree to be turned about its vertical pivot axis. The studs 38 and 39, depending from each of the fixtures 34 and 35, are each provided at the lower end with two superimposed rollers 299 and 29? mounted on ball bearings and disposed to engage the cam surfaces for guiding the work hold-- ing fixtures through the cutting zone. Since the rollers engage the guiding cams with rolling action, the amount of wear on the cams is reduced to a minimum, and consequently, the accuracy of the cams in guiding the work is less likely to be impaired than would be the case if sliding cam followers were used.

As may best be seen in Figure 3, the lower rollers 29'! on both studs 38 and 39 engageand roll upon the straight line guiding cam 49, while thework holding fixture is being moved through thecutting zone. guide the Work holding fixture along a straight line, it will be understood that the work holders may be moved along a curved line or a line having any other shape to effect cutting of the work according to any predetermined configuration by substituting a cam track of the required shape. As best seen in Figures 14 and 15, the upper rollers 296 engage and roll upon the periphery of a central cam 299, which completely encircles the gudgeon bearing I99 and constitutes a cam track for guiding the work holding fixtures as they arebeing moved from the cutting zone through the loading station and back to the cutting zone.

The cam rollers on the studs 38 are disposed concentrically with the bearings 293 and 294, which pivotally support the work holding fixture, and they are maintained in contact with the surface of the cam 299 at all times, by reason of the fact that the cam is shaped to provide a constant diameter at all angular positions. However, the studs 39 are not constrained in this manner to any predetermined path of movement, since the work holders may be pivoted about the axes of the studs 39. In order to retain the upper rollers 299 on the studs 39 in contact with the cam 299, each of the Work supporting fixtures 39 and 35 is provided with a gear segment H I, as shown in Figure 13, which meshes with rack teeth on a rod 2I2 mounted for endwise sliding movement in the slide 31 and provided with a compression spring 2i3 arranged to exert force in direction tending to turn the work holders clockwise, as seen in Figures 13 and 14, to force the rollers 296 on the studs 39 into engagement with the cam 299.

In moving the workpiece through the cutting zone, it is necessary that the work holding fixture be supported as rigidly as possible to prevent any movement which might result in inaccuracies or vibration of the workpiece. For this purpose, the inner cam 299 is provided with a straight line portion 2M, as shown in Figure 14, disposed parallel with and slightly above the straight line guiding cam 49 and in such position that as the lower rollers 291 roll along the cam 49, the upper rollers 296 engage and roll along the straight portion 2M of cam 299, as shown in Figure 3, in manner to positively guide the work holder along the straight line path past the cutter 51. The rollers 299 and 29'! on the studs 38 and 39' are wedged between the cam surfaces 49 and 2M in manner to effect rigid support of the work holding fixtures, and in addition a hydraulic cylinder 2I5 provided with a piston 2I-6 is mounted in the cen- Although the cam 49 is shaped to.-

tral part of the table and is operative to exert a force in the direction tending to move the slide 3! to the right, as seen in Figure 3, to insure firm engagement with the straight line guiding earn 4!! and to prevent any slight tilting movement or vibration of the work holder which might other-- wise occur, by reason of clearances in the bearings supporting the work fixture and the rollers.

Since the work holding fixture does not move along a straight line until after the rollers on both the stud 38 and the stud 39 engage the straight cams 46 and 2M, the length of the straight line path of movement is shorter than the straight portion 2! 4 of the cam 20!! by an amount equal to the distance between the centers of the studs. The length of the straight line path of movement is indicated in Figures 2 and 14 by the dimension E, and since the work holding fixture is mounted concentric with the leading stud 38, the straight line motion does not begin until the work holder has moved along the cam 4!! far enough to bring the rollers 26! on the trailing stud 39 into engagement with the straight line cam 46. Consequently, the straight line path of movement is oifset somewhat relative to a vertical plane longitudinally of the machine through the center of the rotating table, as appears in Figures 2 and 14. In order that advantage may be taken of the full length of the straight line movement, the cutter spindle 32 is correspondingly offset relative to the center of the table 33, as best shown in Figure 2. Further, in order that the spindle 32 may be positioned to rigidly support the cutter as near as possible to the straight line cutting zone E, the spindle carrying head 42 is provided with a forwardly projecting or overhanging supporting portion 2 !8, as shown in Figures 1, 2, and 3, which is disposed to overlie the outer edge of the rotating table 33, in order to support the cutter spindle at a position as near as possible to the work.

Each of the work holding fixtures 34 and 35 is arranged to carry asuitable work clamping device such as a vise 226. As shown in Figures 1, 2, 3, 11 and 15, the vises 226 are mounted on the respective work holding fixtures in manner to be adjusted angularly thereon and are secured in adjusted position by means of bolts 22!, the

heads of which engage circular T-slots 222 in the upper surfaces of the fixtures. Referring particularly to Figures 2, 3, and 15, each of the Vises includes a body portion 224 carrying a fixed jaw 225 and a slidable jaw 223 arranged for relative cooperating movement to efiect clamping of workpieces therebetween, the movable jaw 226 being carried by a sliding member or slide 221.

In operating the machine a workpiece is placed between the fixed jaw and the movable jaw while the fixture is in the loading position, and then as it moves toward the cutting zone, the work is automatically clamped by hydraulic pressure means. For this purpose, each work holding fixture is provided with a central vertically disposed hydraulic cylinder 23!) provided with a piston 23! having an upwardly extending piston rod 232, which engages a roller 233 on one end of a pivoted lever 234 mounted in the vise. When pressure is admitted to the cylinder 230 to move the piston 23! upward, the piston rod 232 pivots the lever 234 counter-clcckwisaas appears in Figure 15, causing a lug 235 thereon to engage a notch in the slide 22'! in manner to move the jaw 226 toward the jaw 225.

The relative positions of the jaws 225 and 226 may be adjusted to adapt them to clamp a workpiece of predetermined size. This adjustment may be effected by moving the jaw 226relative to the slide 22! to engage depending teeth 236 on the jaw in any one of a plurality of notches 23'i in the slide 221, as shown in Figure 15, to constitute a rough adjustment, the jaw being retained on the slide by tightening a bolt 238. To provide for effecting a fine adjustment, the fixed jaw 225 is carried by a bracket 239 provided on its lower face with serrations 240, which engage complementary serrations 24! in the upper face of the vise body 224, as shown in Figures 2 and 11. The bracket 239 is provided with an adjusting screw 242, which engages the back of the jaw member 225 for moving it precisely to the desired position, bolts 243 being provided for clamping both the jaw 225 and the bracket 239 to the vise body 224 in the adjusted position.

When the clamping pressure in the cylinder 23!! is released, a tension spring 245 draws the piston 23! downward in the cylinder 236, and a spring 246 in the vise body moves the sliding member 22! in direction to withdraw the movable jaw 226 from the stationary jaw 225. When relatively small workpieces are being machined, it is desirable to limit the extent of opening of the jaws to prevent the workpieces from dropping into the opening between them. For this purpose, a stop member 246 (Figure 15) is adjustably fastened to the sliding member 22'! by screws 249, in manner to engage the vise body 224 when the jaws have been opened to the predetermined position. In the event that a clamping or holding arrangement other than an automatically actuated vise is to be utilized, a plate or the like may be secured to the top of the work holding fixture in position to retain the piston rod 232 and the piston 23! in retracted position within the cylinder 230, the hydraulic pressure being admitted as usual to the cylinder without effecting movement of the piston.

Hydraulic pressure for actuating the stabilizing piston 2!6 and the vise clamping pistons 23! is derived from pumps 264 and 265, which are mounted in and carried bodily by the gudgeon 36. By this arrangement, the hydraulic pressure may be conducted to the cylinders by means of comparatively short passageways, and the control of the system may be efiected by a valve mechanism formed in the gudgeon 36 and its cooperating bearing sleeve N6, the valve being operative to effect movement of the actuating pistons in accordance with the angular position of the table 33. As may be seen in Figures 3, 11, 21 and 22, the pumps 264 and 265 are of the gear type and are mounted one above the other with the driving gears thereof disposed in alignment and concentrically with the axis of rotation of the table supporting gudgeon, the arrangement being such that a shaft 236, connected with both of the driving gears, extends concentrically through the gudgeon 36 and depends therefrom to provide a driving connection for actuating both pumps.

The pump driving shaft 266 coupled to a horizontally disposed worm wheel 26'! that is journalled in the bed 36 in meshing engagement with a driving worm 238, as appears in Figure 4. The pump driving worm 268 is operatively connected for rotation with the rapid traverse rate driving Worm !6'! by means of a key 266 carried by the body of the dashpot H9, the connection being such that both the pump 25 i and the pump 265 are driven whenever the motor 6! is operating. As shown in Figure 11, the pumps 264 and 2'65- aresupplied with actuating liquid such as ordinary lubricating oil, from a sump 2'' through a suction pipe 212, the oil from the pumps being distributed under pressure to thevarious parts of the machine in well known manner for effecting lubrication of the mechanism inaddition to serving as actuating liquid for the hydraulic cylinders.

When the motor is operating and the pumps 2 6-4, and 265 are functioning, as previously mentiorred with reference tothe hydraulic apparatus shown in Figure 11, the oil drawn from the sump 2' through the pipe 212 passes into an annular groove 28! in the bearing sleeve I95, which communicates at all times with a passageway 282 in the gudgeon 36 that leads to the pumps. From the pump 265, the oil is forced under pressure through a passageway 283 (Figures 11 and 22) leading to a pressure regulating or relief valve 284. Oil in excess of that required to maintain a predetermined operating pressure in the passageway 283 escapes through the relief valve 284 into a passageway 285, which leads to an oil filter 286 (Figure 1) and thence into the lubricating system of the machine.

When the rotary table 33 is in the position shown inthe drawings, with the work holding fixture 35 passing through the cutting zone E, the passageway 28% from the pump 255 is positioned as shown in Figures 11 and 22 to communicate: with a groove 28? in the sleeve which co municates' through passageways 28S with a similar groove 289 at a diametrically opposite position. The groove 289 communicates with a passageway 291 in the gudgeon 3t that passes upwardly through the gudgeon to the stabilizing cylinder 2P5.

As appears in Figure 3', pressure exerted through the passageway 28! enters a narrow groove 292 in the bottom of the cylinder 2H5, which communicates with a port 293 in the piston 2W connecting with a longitudinal passageway 294 therein through which the oil flows to the left end of the cylinder and exerts pressure upon the piston 2 l 6 in direction to move it to the right, in manner to force the slide 3'! to the right, as previously explained, for firmly engaging the cam following rollers on the fixture 35 with the straight line guiding cam 40. Oil from the right end of the cylinder M escapes through a port 295 in the top of the cylinder into a reservoir 29%, which serves to maintain the cylinder full of oil at all times and prevents the entrance of air into the system, the oil' which overflows from the reservoir 296 returning to the sump 2.

The hydraulic system is shown schematically and somewhat more fully in Figure 25, in which the pivot bearing I96 constituting the valvesleeve is shown developed, and the passages in the gudgeon 36 are indicated as tubes superimposed upon the developed sleeve. As there shown, the valve grooves 281 and 289, with which thepassageway 283 from the pump and the passageway 29! to the stabilizing cylinder 2l5 communicates respectively when the valve is in the position shown, appear as relatively short openings connected by the passageways 288 shown dotted along the back of the sleeve. When the table is turned in moving a work fixture out of the cutting zone E, the passageway 283 from the pump 255 moves out of communication with the groove 281, thereby cutting off the pressure to the stabilizing cylinder 2| 5.

As may be seen by referring to Figure- 14, at the time that the work fixture moves out of the" 16 cutting zone, the roller 20!; on the stud 38 thereof passes from the straight line portion 2M= of the cam 289 to an arcuate portion thereof, the: radius of which is such that the work supportin slide 31 assumes a central position on the table 33. Under. this condition, the piston H6 is moved to a central position within the cylinder Hi5, as shown in Figure 26, in which position both the inlet port 292 and the exhaust port 285 are closed. As the table 33 continues to turn. in moving the work fixture to the unloading: position, the piston 2E6 isamoved in the same direction past the center position,. thereby moving. a port 298 into communication. with the inlet port 292 at the time that the passageway 29! inthe g-udgeon moves into communication with the groove 28'! in the sleeve, and the passageway 283 from the pump moves into communication with the groove 289. Further movement of the piston 2H3 then causes oil in the right end of the cylinder 215 to flow through a longitudinal passageway 299 in the piston; which connects with the port 298, and then out through the port 2921 and. back through the passageway 29| against the pressure exerted by the pump 28.5, theexcess oil escaping through the relief valve 284. This expulsion of oil from the. cylinder 2l5' back against the pump pressure occurs most rapidly at the time that the work supporting fixture approaches the cutting zone at rapid traverse rate; consequently, the cylinder 215 and the piston 2L6 function as a dashpot in. checking the speed of the rotary table and in cushioning the transition. from movement at rapid traverse rate to move-- ment at feed rate. By the time thatthe succeeding work supporting fixture 32 has moved. into the cutting zone E at. feed. rate, the piston 2H3 has been moved back by the straight line cam- 40 to the end of its stroke and is beginning tomove forward again under the pressure admitted through the passagewa 23-! and the port 232,. which acts upon thepistonv 2H5 in direction tending. to force the guiding rollers against the straight line cam 40, as previously explained. The piston, being symmetrically formed, functions in the same manner, when moved to either side of the mid-position in which it is shown in Figure 26 and acts with equal efiectiveness upon either work fixture.

Before the rotary table 33 arrives at the point at which a work holding fixture enters the cutting zone, the vise of the work holder is closed to clamp the workpiece, as previously explained. To efiect the clamping operation quickly, a relatively large-volume of actuating liquid is admitted to the cylinder 23E! associated with the vise. this position of the gudgeon the passageway 2-83 from the. pump 26 5 is in communication with anarcuate groove 302 in the sleeve 596, shown in Figures 22 and 25, thereby placing it in communication with a port 303 leading into a passageway 384. The passageway 305 communicates with a groove 385 in the sleeve, which communicates with a passageway 306 leading to the cylinder 230- of the work holding fixture 35.

The pump 265 is of the type adapted to deliver a relatively large quantity of oil at relatively low pressure, and consequently the piston 23! is moved upward at relatively rapid rate to quickly clamp the workpiece lightly in the jaws of the vise. As the work holding fixture 35 enters the cutting zone, the passageway 283 from the pump and the port 303 move-out of communication with the groove 392, as indicated in Figure 25. Under these. conditions, pressure is supplied to the cylinder 230 from the pump 264 which discharges directly into the passageway 304. The pump 264 is of the type supplying a comparatively small quantity'of oil at relatively high pressure, the high pressure oil passing through the passageway 304, the groove 305, and the passageway 306 to the cylinder 230, in manner to exert firm clamping pressure upon the workpiece in the visa In order that the clamping pressure may be adjustedto suit the particular workpiece being clamped, an adjustable pressure regulator 310 is provided and connected in manner shown in Figure 25. As there shown, a passageway 3!! which communicates with the groove 305 leads to a spring pressed pressure regulating plunger 3 I 2 in the regulator 310.

As the work holding fixture 35 moves out of the cutting zone, the passageway 304 moves'out of communication with the groove 305, and an exhaust passageway 3l4 moves into communication with the groove 305, thereby permitting the escape of oil from cylinder 230 through the passageway 306 and groove 305, into passageway 3l4,

"The discharge passageway 283 for the pump 265 next moves into communication with a groove 3 l 6 similar to and diametrically dis-posed from the groove 302, which again places it in communication with the port 303 and the passageway 304. The passageway 304 is then in communication with a groove 3 l 1, which connects it to a passageway 3| 8 leading to the cylinder 230 associated with the work holding fixture 34, in manner to quickly fill this cylinder with low pressure oil. After the port 303 moves out of communication with the groove 3l6, high pressure oil from the pump 264 passes through the passageway 304, the groove 311, and thepassageway 3I8, in manner to exert clamping pressure upon the piston 23l. 7

From the groove 3, a passageway 3l9 leads to the pressure regulator 3l0, where it communicates with another spring pressed regulating plunger 320. The springs of both the plunger 3l2 and the plunger 320 may be regulated simultaneously by turning a hand wheel 32 l which has a screw thread connection with an adjusting block 322 that engages both the springs. By this arrangement, the clamping pressures exerted upon the two clamping pistons may be adjusted simultaneously to eiTect the same clamping pressure in both the Vises, the two systems being maintained independent of each other to provide for release of excessive pressure from either clamping cylinder at any time, the liquid in excess of that required to maintain the predetermined pressure escaping through a pas-sageway 323, which is arranged to discharge into the sump 2'.

In order that the clamping pressure in the cylinders may be ascertained readily, a pressure gauge 330 is provided on the machine and connected in manner to indicate the pressure being exerted upon the active clamping piston. For this purpose, a passageway 33l connected with the passageway 3| I, and a passageway 332 connected with the passageway 319, lead to opposite ends of a ball valve mechanism 333 to the center of which the pressure gauge 330 is connected by a passageway 334. A ball 335, which is free to move lengthwise of the chamber within the valve 333, permits the oil to flow from whichever line may be under pressure to the gauge 330, but pre- 18 vents the oil from passing through the valve into the other line.

The passageways 306 and 318, which lead from the grooves 305 and 3 I 1, respectively, to the cylinders 230, associated with the work holdin fixtures 34 and 35, are each formed partly in the gudgeon 36, as shown in Figure 11 and constituted partly by a flexible connecting member arranged for establishing connection from the gudgeon to the relatively movable work support' The flexible connecting mechanism includes a hollow stud 340 depending from the table 33 and connected to the passageway extending through the gudgeon, as shown in Figure 11, with regard to the passageway 306. The stud 340 is pivotally connected to a hollow block 34! arranged to slidingly receive a tube 342, as best shown in Figures 14 and 15, which is provided with an enlarged head 343 that is rotatably secured to the lower end of the stud 38 constituting the pivot axis of one of the work holding fixtures. As appears in the drawing, the stud 38 is formed hollow to provide communication with the cylinder 230, which is disposed concentrically therewith.

As a modification, the mechanism for prolonging the feed rate movement of the table to lengthen the loading period may be constituted as part of the hydraulic system, being arranged to be actuated hydraulically, as shown in Figures 23 and 24. As there shown, the actuating pedal IT! is pivotally mounted upon a control unit 346, which may be attached to the front of the machine, and is operatively connected to an arm 34'! within the unit, which engages one end of a spring pressed valve plunger 348. When the pedal 1' is depressed, the valve plunger is moved upward within a cooperating valve casing 340 to a position in which a groove 350 on the plunger efiects a connection between a passageway 35! leading from a pump which may be taken to represent one of the pumps mounted in the gudgeon 36 or any other suitable source of pressure, and a passageway 352 leading to a plunger actuating cylinder 353. Within the cylinder 353, the pressure fluid acts upon a piston 354, which is provided with a hollow piston rod 355 corresponding with the plunger l'll, shown in Figure 12 and carrying at its forward end the spring-urged roller I84 which is adapted to enter beneath the shifting collar l3l, as shown in Figure 24, when the piston 354 is moved forward within the cylinder 353 by the pressure fluid. When the pedal I'll is released, the valve plunger 348 is moved downward by a spring 351, thereby cutting on" communication with the pressure passageway 352 and establishing communication with an exhaust passageway 358 in manner to permit the pressure to escape from the cylinder 353. A spring 359 in the cylinder 353 then moves the piston to the right, as shown in Figure 23, in manner to withdraw the roller I84 from beneath the shifting collar 13!, thereby permitting it to move downward and shift the drive mechanism in direction to engage the rapid traverse drive.

The electric driving motor 6| is controlled by means of push buttons mounted in 'a convenient location at the front of the machine, as shown in Figures 1 and 2. As appears in Figures 1 and 2, the front of the cutting zone is guarded by means of a glass shield 428, which extends across the machine between the two front corner posts 424 and 426. This shield is more fully described and claimed in copending application, Serial No.

19 543,681, filed July 6, 1944, now Patent No. 2,443,734, granted June 22, 1948.

Another type of work clamping device for mounting on the work holding fixtures 34 and 35 is illustrated in Figures 16 and 17. This device is designated generally by the reference numeral 4 10, and it is generally similar to and constitutes a modification of the vise 220, shown mounted on the machine in Figures 1, 2, and 3. The modified vise M0 is adapted to be mounted on a work holding fixture for angular adjustment in manner similar to that in which the vise 220 is mounted, and it comprises essentially a body portion 444 carrying a fixed jaw 445 and a slidable relatively movable jaw 446, a pivoted lever 448, similar to the lever 234 in the vise 220, being provided for engagement by the actuating piston rod 232 for moving the jaw 446 toward the jaw 445, in the manner previously explained in connection with the vise 220, for clamping a workpiece therebetween.

The modified vise 44D differs from the previously described vise 226 primarily in that a compression spring 450 is provided for urging the vise jaws together to lightly clamp a workpiece prior to the application of. the hydraulic clamping pressure. As may be seen in Figure 1'7, the spring 450 acts upon the movable clamping jaw M6 in direction tending to urge it toward the fixed jaw 445, an adjusting plug 45I being provided for adjusting the tension of the spring. In order to remove a workpiece from the vise 440, manually actuated means are provided for overcoming the clamping force of the spring 450.

For this purpose, an actuating eccentric or cam 453 is rotatably mounted in the body 444 of the vise and is provided with an actuating hand lever 454, the arrangement being such that when the lever 454 is turned from the position shown in full lines in Figure 16 to the dotted line position, the eccentric 453 is turned in manner to engage the slide carrying the movable jaw 446 and move it away from the fixed jaw 445 against the resistance of the spring 450. After a finished Workpiece has been removed and a new workpiece placed in the vise, the hand lever 454 is moved back to the position shown in full lines, thereby releasing the movable vise jaw and permitting the spring 458 to exert force for clamping the workpiece lightly between the jaws. With the workpiece thus held in position in the vise, the work carrying table may be rotated to move it toward the cutting zone, whereupon fluid pressure may be applied to firmly clamp the workpiece, as previously described.

From the foregoing description of an illustrative milling machine embodying this invention, it is apparent that there has been provided apparatus, which is capable of rapidly and automatically effecting machining of successive workpieces in a substantially continuous operation. As more fully explained hereinbefore, the machine is arranged to receive workpieces at a loading station at the forward edge of a rotary table, automatically clamp them, and quickly move the workpieces into cutting position by rotating the table at rapid traverse rate. The workpieces are then fed past the cutter along a straight line by turning the table at feed rate and guiding the work holder by means of a cam fixed in the machine bed. After the cutting operation has been completed, the workpieces are led away from the cutting zone without returning them past the cutter, by continuing the rotation of the table invention has further provided improved clutching mechanism, including selectively operable roller clutches for controlling rotation of the table, and improved hydraulic and electrical control systems for effecting control of the various functions of the machine, as well as other improvements in mechanisms and structural features tending to improve generally the efficiency and reliability of milling machines.

Although the foregoing description and the accompanying drawing have set forth the present invention for the most part in one exemplary mechanism, it is to be understood that the structure shown and described is intended only to be illustrative of an operative embodiment of the invention, and that it is contemplated that the various features may be incorporated in other structures, without departing from the spirit and scope of the invention, as defined in the subjoined claims.

The invention is hereby claimed as follows:

1. In a machine tool, the combination with a frame and a work supporting table movably mounted on said frame, of fluid pressurev actuated clamping means mounted onv said table for holding workpieces while being machined, a source of fluid pressure mounted on said table and conduit means including relatively movable co.- operating valve elements carried by said frame and said table respectively and constituting selectively operating connecting means between said pressure source and said clamping means. on said table, said valve elements being arranged to. effect clamping of a workpiece in said clamping means when said table is in one position and unclamping thereof when said table is in another position, whereby workpieces may be securely held while being carried by said table through. a cutting zone and then automatically unclamped after being machined.

2. In a machine tool having a frame, driving means supported in said frame, and a rotatable table mounted on said frame, the combination with hydraulically actuated means carried by said rotatable table and movable bodily therewith, of

a pump carried bodily by said rotatable table,.

transmission means operatively connecting said driving means to said table to rotate it, transmission means operatively connecting said driving means to said pump in manner to operate it independently of rotation of said table, and a hydraulic circuit operatively connecting said pump to said hydraulically actuated means on said table, said circuit including means operative in response to rotation of said table for controlling said hydraulically actuated means.

3. In a hydraulicsystem, the combination with a sleeve constituting one element of a control valve and a gudgeon movably mounted within said sleeve and constituting the cooperating element of said valve, of a pump mounted within said gudgeon and movable bodily therewith, said pump being operatively connected to provide fluidpressure to said control valve, whereby hydraulically actuated mechanism movable bodily-with said gudgeon may be operatively connected directly to said valve for actuation by said pump in accordance with the position of said gud'geon relative to said sleeve.

4. In a machine tool, the combination with a frame and a cutting tool carried by said frame,

of a work-supporting table having a gudgeon-rotatably journalled in said frame, means to. rotate said table to move workpieces carried thereby in the same direction at rapid traverse rate. The 7 into engagement with said cutting tool, hydrau- 

